Air conditioning system and air conditioner having the same

ABSTRACT

An air conditioning system and an air conditioner having the same are provided. The air conditioning system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, a directional control assembly, a first throttling element, a second throttling element, a gas-liquid separator and a liquid reservoir. The compressor comprises a first cylinder, a second cylinder, an exhaust port and a gas return port; an exhaust volume ratio of the second cylinder to the first cylinder is less than or equal to 0.1. The directional control assembly comprises a first valve port, a second valve port, a third valve port and a fourth valve port; when the air conditioning system is refrigerating, the first valve port is in communication with the second valve port, and the third valve port is in communication with the fourth valve port; when the air conditioning system is heating, the first valve port is in communication with third valve port, the second valve port is in communication with the fourth valve port, and a gas outlet of the gas-liquid separator is in communication with the second cylinder.

CROSS-REFERENCE TO RELATED APPLICATION

The present application is a national phase entry under 35 USC § 371 of International Application PCT/CN2016/079057, filed Apr. 12, 2016, which claims the benefit of prior Chinese Application No. 201510662023.3 filed Oct. 10, 2015 and No. 201520793811.1 filed Oct. 10, 2015. The entire disclosures of which are incorporated herein by reference.

FIELD

The present disclosure relates to a technical field of refrigeration devices, and more particularly to an air conditioning system and an air conditioner having the same.

BACKGROUND

In the related art, an air conditioning system designed for a rated refrigerating work condition, an intermediate refrigerating work condition, a rated heating work condition, an intermediate heating work condition and a low-temperature heating work condition of a Chinese APF standard, and an air conditioning system designed for a North American SEER work condition, a HSPF work condition, a European work condition, a Japanese work condition and a ultralow-temperature heating work condition, lack an optimal design, so that an exhaust volume ratio of a first cylinder and a second cylinder of a designed compressor is not within the optimal range, which results in an adverse effect on the overall performance of the air conditioner.

SUMMARY

The present invention seeks to solve at least one of the problems existing in the related art to at least some extent. To this end, the present invention provides an air conditioning system with an advantage of a good use performance.

The present invention also provides an air conditioner having the above-mentioned air conditioning system.

According to a first aspect of embodiments of the present invention, an air conditioning system is provided and includes a compressor comprising a first cylinder, a second cylinder, an exhaust port and a gas return port, a gas compressed by the first cylinder and the second cylinder being discharged from the exhaust port, in which an exhaust volume of the first cylinder is V1, an exhaust volume of the second cylinder is V2, and the V1 and V2 meet: V2/V1≤0.1; an outdoor heat exchanger comprising a first inlet and a first outlet, and an indoor heat exchanger comprising a second inlet and a second outlet, the first outlet being in communication with the second inlet; a directional control assembly comprising a first valve port, a second valve port, a third valve port and a fourth valve port, in which the first valve port is in communication with the exhaust port, the fourth valve port is in communication with the gas return port, the second valve port is in communication with first inlet, the third valve port is in communication with the second outlet; a first throttling element and a second throttling element connected in series between the indoor heat exchanger and the outdoor heat exchanger; a gas-liquid separator comprising a first opening, a second opening and a gas outlet, in which when the air conditioning system is refrigerating, the first valve port is in communication with the second valve port, the third valve port is in communication with the fourth valve port, the first opening is in communication with the first throttling element, the second opening is in communication with the second throttling element, and the gas outlet is in communication with the second cylinder via a medium-pressure suction pipe; when the air conditioning system is heating, the first valve port is in communication with the third valve port, the second valve port is in communication with the fourth valve port, the first opening is in communication with the second cylinder via the medium-pressure suction pipe, the first opening is in communication with the first throttling element, and the gas outlet is in communication with the second throttling element; and a liquid reservoir, in which one end of the liquid reservoir is in communication with the fourth valve port, and the other end thereof is in communication with the gas return port via a low-pressure suction pipe.

For the air conditioning system according to embodiments of the present invention, by making the exhaust volume ratio of the second cylinder to the second cylinder smaller than or equal to 0.1, the performance of the air conditioning system may be effectively improved, and the air conditioner may reach a state with the optimal energy efficiency easily.

In some embodiments of the present invention, the exhaust volume of the first cylinder is V1, the exhaust volume of the second cylinder is V2, and the V1 and V2 meet: V2/V1≤0.09.

In some embodiments of the present invention, the exhaust volume of the first cylinder is V1, the exhaust volume of the second cylinder is V2, and the V1 and V2 meet: 0.04≤V2/V1≤0.08.

In some embodiments of the present invention, the exhaust volume of the first cylinder is V1, the exhaust volume of the second cylinder is V2, and the V1 and V2 meet: 0.04≤V2/V1≤0.07. In some embodiments of the present invention, the exhaust volume of the first cylinder is V1, the exhaust volume of the second cylinder is V2, and the V1 and V2 meet: 0.07<V2/V1≤0.08.

In some embodiments of the present invention, the directional control assembly is a four-way valve.

In some embodiments of the present invention, the compressor is a gaseous refrigerant injection type compressor.

According to a second aspect of the present disclosure, an air conditioner is provided and includes the above-described air conditioning system.

For the air conditioner according to embodiments of the present invention, by providing the above-described air conditioning system and making the exhaust volume ratio of the second cylinder to the first cylinder smaller than or equal to 0.1, the performance of the air conditioning system may be effectively improved, and the air conditioner may reach the state with the optimal energy efficiency easily.

BRIEF DESCRIPTION OF THE DRAWINGS

These and/or other aspects and advantages of embodiments of the present invention will become apparent and more readily appreciated from the following descriptions made with reference to the drawings, in which:

FIG. 1 is a schematic view of an air conditioning system according to an embodiment of the present invention;

FIG. 2 is a schematic view of an air conditioning system according to an embodiment of the present invention, in which the air conditioning system is in a refrigerating state.

FIG. 3 is a schematic view of an air conditioning system according to an embodiment of the present invention, in which the air conditioning system is in a heating state.

REFERENCE NUMERALS

-   -   100: air conditioning system,     -   110: compressor, 111: exhaust port, 112: gas return port,     -   120: outdoor heat exchanger, 121: first inlet, 122: first         outlet,     -   130: indoor heat exchanger, 131: second inlet, 132: second         outlet,     -   140: directional control assembly, 141: first valve port, 142:         second valve port, 143: third valve port, 144: fourth valve         port,     -   150: first throttling element, 160: second throttling element,     -   170: gas-liquid separator, 171: first opening, 172: second         opening, 173: gas outlet,     -   181: liquid reservoir, 182: medium-pressure suction pipe, 183:         low-pressure suction pipe.

DETAILED DESCRIPTION

Embodiments of the present invention will be described in detail and examples of the embodiments will be illustrated in the drawings, in which same or similar reference numerals are used to indicate same or similar members or members with same or similar functions throughout the specification. The embodiments described herein with reference to drawings are explanatory, which are used to illustrate the present invention, but shall not be construed to limit the present invention.

In the description of the present inventor, it is to be understood that terms such as “central”, “upper”, “lower”, “front”, “rear”, “vertical”, “horizontal”, “top”, “bottom”, “inner”, and “outer” should be construed to refer to the orientation as then described or as shown in the drawings under discussion. These relative terms are for convenience and simplification of description of the present disclosure, and do not alone indicate or imply that the device or element referred to must have a particular orientation, and must be constructed or operated in a particular orientation, thus it should not be construed to a limit to the present disclosure. In addition, terms such as “first”, and “second” are used herein for purposes of description and are not intended to indicate or imply relative importance or significance or to imply the number of indicated technical features. Thus, the feature defined with “first” and “second” may explicitly or implicitly comprise one or more of this feature. In the description of the present invention, “a plurality of” means two or more than two, unless specified otherwise.

In the description of the present inventor, it is to be noted that unless specified or limited otherwise, the terms “mounted,” “connected,” and “coupled” are used broadly, and may be, for example, fixed connections, detachable connections, or integral connections; may also be mechanical or electrical connections; may also be direct connections or indirect connections via intervening structures; may also be inner communications of two elements, which can be understood by those skilled in the art according to specific situations.

An air conditioning system 100 according to embodiments of the present invention will be described below referring to FIGS. 1 to 3.

As shown in FIGS. 1 to 3, an air conditioning system 100 according to embodiments of the present invention includes a compressor 110, an indoor heat exchanger 130, an outdoor heat exchanger 120, a directional control assembly 140, a first throttling element 150, a second throttling element 160, a gas-liquid separator 170 and a liquid reservoir 181.

Specifically, the compressor 110 may include a first cylinder (not illustrated), a second cylinder (not illustrated), an exhaust port 111 and a gas return port 112, and a gas compressed by the first cylinder and the second cylinder may be discharged from the exhaust port 111; an exhaust volume of the first cylinder is V1, an exhaust volume of the second cylinder is V2, and V1 and V2 meet: V2/V1≤0.1.

As shown in FIG. 1, the outdoor heat exchanger 120 includes a first inlet 121 and a first outlet 122, the indoor heat exchanger 130 includes a second inlet 131 and a second outlet 132, and the first outlet 122 is in communication with the second inlet 131. One end of the liquid reservoir 181 is in communication with a fourth valve port 144, and the other end thereof is in communication with the gas return port 112 via a low-pressure suction pipe 183. The directional control assembly 140 may include a first valve port 141, a second valve port 142, a third valve port 143 and the fourth valve port 144, in which the first valve port 141 is in communication with the exhaust port 111, the fourth valve port 144 is in communication with the gas return port 112, the second valve port 142 is in communication with the first inlet 121, and the third valve port 143 is in communication with the second outlet 132.

A first throttling element 150 and a second throttling element 160 are connected in series between the indoor heat exchanger 130 and the outdoor heat exchanger 120. A gas-liquid separator 170 may include a first opening 171, a second opening 172 and a gas outlet 173; the first opening 171 is in communication with the first throttling element 150, the second opening 172 is in communication with the second throttling element 160, and the gas outlet 173 is in communication with the second cylinder. The gas-liquid separator 170 may separate a refrigerant therein into a gaseous refrigerant and a liquid refrigerant; the gaseous refrigerant may flow out through the gas outlet 173, and the liquid refrigerant may flow out through the second opening 172. It should be noted that: after experimental validation, by making the exhaust volume ratio of the second cylinder to the second cylinder smaller than or equal to 0.1, the performance of the air conditioning system 100 may be effectively improved, and the air conditioner may reach a state with the optimal energy efficiency.

As shown in FIG. 2, when the air conditioning system 100 is refrigerating, the first valve port 141 is in communication with the second valve port 142, and the third valve port 143 is in communication with the fourth valve port 144. The refrigerant in the liquid reservoir 181 is sucked into the first cylinder and the second cylinder by the compressor 110, and then enters the first valve port 141 via the exhaust port 111 along a direction shown by arrow a1 in FIG. 2 after compressed by the first cylinder and the second cylinder. As the first valve port 141 is in communication with the second valve port 142 and the second valve port 142 is in communication with the first inlet 121, the refrigerant may pass through the second valve port 142 and the first inlet 121 successively, and then enter the outdoor heat exchanger 120 along a direction shown by arrow a2 in FIG. 2. The refrigerant enters the first throttling element 150 via the first outlet 122 along a direction shown by arrow a3 in FIG. 2 after heat exchange in the outdoor heat exchanger 120, and flows from the first throttling element 150 into the gas-liquid separator 170 via first opening 171 along a direction shown by arrow a4 in FIG. 2 after throttled by the first throttling element 150.

The gas-liquid separator 170 may separate the refrigerant therein into a gaseous refrigerant and a liquid refrigerant; the gaseous refrigerant may flow from the gas outlet 173 into the second cylinder via a medium-pressure suction pipe 182 along a direction shown by arrow a41 in FIG. 2, and the liquid refrigerant may flow from the second opening 172 into the second throttling element 160 along a direction shown by arrow a42 in FIG. 2. The refrigerant enters the indoor heat exchanger 130 via the second inlet 131 along a direction shown by arrow a5 in FIG. 2 after throttled by the second throttling element 160. The refrigerant flows from the second outlet 132 of the indoor heat exchanger 130 into the third valve port 143 along a direction shown by arrow a6 in FIG. 2 after heat exchange in the indoor heat exchanger 130. As the third valve port 143 is in communication with the fourth valve port 144 and the fourth valve port 144 is in communication with the liquid reservoir 181, the refrigerant may flow into the liquid reservoir 181 via the fourth valve port 144 along a direction shown by arrow a7 in FIG. 2, and further flow back into the compressor 110 again via the gas return port 112.

As shown in FIG. 3, when the air conditioning system 100 is heating, the first valve port 141 is in communication with third valve port 143, and the second valve port 142 is in communication with the fourth valve port 144. The refrigerant in the liquid reservoir 181 is sucked into the first cylinder and the second cylinder by the compressor 110, and then enters the first valve port 141 via the exhaust port 111 along a direction shown by arrow b1 in FIG. 3 after compressed by the first cylinder and the second cylinder. As the first valve port 141 is in communication with the third valve port 143 and the third valve port 143 is in communication with the second outlet 132, the refrigerant may pass through the third valve port 143 and the second outlet 132 successively, and then enter the indoor heat exchanger 130 along a direction shown by arrow b2 in FIG. 3. The refrigerant enters the second throttling element 160 via the second inlet 131 along a direction shown by arrow b3 in FIG. 3 after heat exchange in the indoor heat exchanger 130, and flows from the second throttling element 160 into the gas-liquid separator 170 via the gas outlet 173 along a direction shown by arrow b4 in FIG. 3 after throttled by the second throttling element 160.

The gas-liquid separator 170 may separate the refrigerant therein into a gaseous refrigerant and a liquid refrigerant; the gaseous refrigerant may flow from the first opening 171 into the second cylinder via the medium-pressure suction pipe 182 along a direction shown by arrow b41 in FIG. 3, and the liquid refrigerant may flow from the second opening 172 into the first throttling element 150 along a direction shown by arrow b42 in FIG. 3. The refrigerant enters the outdoor heat exchanger 120 via the first outlet 122 along a direction shown by arrow b5 in FIG. 3 after throttled by the first throttling element 150. The refrigerant flows from the first inlet 121 of the outdoor heat exchanger 120 into the second valve port 142 along a direction shown by arrow b6 in FIG. 3 after heat exchange in the outdoor heat exchanger 120. As the second valve port 142 is in communication with the fourth valve port 144 and the fourth valve port 144 is in communication with the liquid reservoir 181, the refrigerant may flow into the liquid reservoir 181 via the fourth valve port 144 along a direction shown by arrow b7 in FIG. 3, and further flow back into the compressor 110 again via the gas return port 112.

For the air conditioning system 100 according to embodiments of the present invention, by making the exhaust volume ratio of the second cylinder to the first cylinder smaller than or equal to 0.1, the performance of the air conditioning system 100 may be effectively improved, and the air conditioner may reach a state with the optimal energy efficiency easily.

According to an embodiment of the present invention, an exhaust volume of the first cylinder is V1, an exhaust volume of the second cylinder is V2, and V1 and V2 meet: V2/V1-0.09. After experimental validation, when the ratio of the exhaust volume V2 of the second cylinder to the exhaust volume V1 of the first cylinder is within the range of less than or equal to 0.09, the use performance of the air conditioning system 100 may be effectively improved, and the air conditioning system 100 may reach the state with the optimal energy efficiency easily. Further, when V1 and V2 meet: 0.04≤V2/V1≤0.08, the use performance of the air conditioning system 100 may be effectively improved, and the air conditioning system 100 may reach the state with the optimal energy efficiency easily.

According to an embodiment of the present invention, when V1 and V2 meet: 0.04≤V2/V1≤0.07, the use performance of the air conditioning system 100 may be effectively improved, and the air conditioning system 100 may reach the state with the optimal energy efficiency easily. According to another embodiment of the present invention, when V1 and V2 meet: 0.07<V2/V1≤0.08, the use performance of the air conditioning system 100 may be effectively improved, and the air conditioning system 100 may reach the state with the optimal energy efficiency easily.

According to an embodiment of the present invention, the compressor 110 may be a gaseous refrigerant injection type compressor 110, such that the performance of the compressor 110 is improved, and the use performance of the air conditioning system 100 is satisfied. According to another embodiment of the present invention, the directional control assembly 140 may be a four-way valve, such that the structure of the air conditioning system 100 may be simplified, and the production cost may be reduced.

The air conditioning system 100 according to embodiments of the present invention will be described below in detail in a specific embodiment referring to FIGS. 1 to 3. It should be appreciated that: the following description is only an exemplary illustration, but not a specific limit to the present invention.

As shown in FIGS. 1 to 3, the compressor 110 is the gaseous refrigerant injection type compressor 110, and includes the first cylinder, the second cylinder, the exhaust port 111 and the gas return port 112; the gas compressed by the first cylinder and the second cylinder is discharged from the exhaust port 111. The outdoor heat exchanger 120 includes the first inlet 121 and the first outlet 122, the indoor heat exchanger 130 includes the second inlet 131 and the second outlet 132, and the first outlet 122 is in communication with the second inlet 131. One end of the liquid reservoir 181 is in communication with the fourth valve port 144, and the other end thereof is in communication with the gas return port 112 via the low-pressure suction pipe 183.

The directional control assembly 140 is a four-way valve, and includes the first valve port 141, the second valve port 142, the third valve port 143 and the fourth valve port 144, in which the first valve port 141 is in communication with the exhaust port 111, the fourth valve port 144 is in communication with the gas return port 112, the second valve port 142 is in communication with the first inlet 121, and the third valve port 143 is in communication with the second outlet 132.

The outdoor heat exchanger 120, the first throttling element 150, the gas-liquid separator 170, the second throttling element 160 and the indoor heat exchanger 130 are successively connected. The gas-liquid separator 170 may include the first opening 171, the second opening 172 and the gas outlet 173; the first opening 171 is in communication with the first throttling element 150, the second opening 172 is in communication with the second throttling element 160, and the gas outlet 173 is in communication with the second cylinder.

As shown in FIG. 2, when the air conditioning system 100 is refrigerating, the first valve port 141 is in communication with the second valve port 142, and the third valve port 143 is in communication with the fourth valve port 144. The refrigerant in the liquid reservoir 181 is sucked into the first cylinder and the second cylinder by the compressor 110, and then enters the first valve port 141 via the exhaust port 111 along the direction shown by arrow a1 in FIG. 2 after compressed by the first cylinder and the second cylinder. As the first valve port 141 is in communication with the second valve port 142 and the second valve port 142 is in communication with the first inlet 121, the refrigerant may pass through the second valve port 142 and the first inlet 121 successively, and then enter the outdoor heat exchanger 120 along the direction shown by arrow a2 in FIG. 2. The refrigerant enters the first throttling element 150 via the first outlet 122 along the direction shown by arrow a3 in FIG. 2 after heat exchange in the outdoor heat exchanger 120, and flows from the first throttling element 150 into the gas-liquid separator 170 via first opening 171 along the direction shown by arrow a4 in FIG. 2 after throttled by the first throttling element 150.

The gas-liquid separator 170 may separate the refrigerant therein into a gaseous refrigerant and a liquid refrigerant; the gaseous refrigerant may flow from the gas outlet 173 into the second cylinder via a medium-pressure suction pipe 182 along the direction shown by arrow a41 in FIG. 2, and the liquid refrigerant may flow from the second opening 172 into the second throttling element 160 along the direction shown by arrow a42 in FIG. 2. The refrigerant enters the indoor heat exchanger 130 via the second inlet 131 along the direction shown by arrow a5 in FIG. 2 after throttled by the second throttling element 160. The refrigerant flows from the second outlet 132 of the indoor heat exchanger 130 into the third valve port 143 along the direction shown by arrow a6 in FIG. 2 after the heat exchange in the indoor heat exchanger 130. As the third valve port 143 is in communication with the fourth valve port 144 and the fourth valve port 144 is in communication with the liquid reservoir 181, the refrigerant may flow into the liquid reservoir 181 via the fourth valve port 144 along the direction shown by arrow a7 in FIG. 2, and further flow back into the compressor 110 again via the gas return port 112.

As shown in FIG. 3, when the air conditioning system 100 is heating, the first valve port 141 is in communication with third valve port 143 and the second valve port 142 is in communication with the fourth valve port 144. The refrigerant in the liquid reservoir 181 is sucked into the first cylinder and the second cylinder by the compressor 110, and then enters the first valve port 141 via the exhaust port 111 along the direction shown by arrow b1 in FIG. 3 after compressed by the first cylinder and the second cylinder. As the first valve port 141 is in communication with third valve port 143 and the third valve port 143 is in communication with the second outlet 132, the refrigerant may pass through the third valve port 143 and the second outlet 132 successively, and then enter the indoor heat exchanger 130 along the direction shown by arrow b2 in FIG. 3. The refrigerant enters the second throttling element 160 via the second inlet 131 along the direction shown by arrow b3 in FIG. 3 after the heat exchange in the indoor heat exchanger 130, and flows from the second throttling element 160 into the gas-liquid separator 170 via the gas outlet 173 along the direction shown by arrow b4 in FIG. 3 after throttled by the second throttling element 160.

The gas-liquid separator 170 may separate the refrigerant therein into a gaseous refrigerant and a liquid refrigerant; the gaseous refrigerant may flow from the first opening 171 into the second cylinder via the medium-pressure suction pipe 182 along the direction shown by arrow b41 in FIG. 3, and the liquid refrigerant may flow from the second opening 172 into the first throttling element 150 along the direction shown by arrow b42 in FIG. 3. The refrigerant enters the outdoor heat exchanger 120 via the first outlet 122 along the direction shown by arrow b5 in FIG. 3 after throttled by the first throttling element 150. The refrigerant flows from the first inlet 121 of the outdoor heat exchanger 120 into the second valve port 142 along the direction shown by arrow b6 in FIG. 3 after the heat exchange in the outdoor heat exchanger 120. As the second valve port 142 is in communication with the fourth valve port 144 and the fourth valve port 144 is in communication with the liquid reservoir 181, the refrigerant may flow into the liquid reservoir 181 via the fourth valve port 144 along the direction shown by arrow b7 in FIG. 3, and further flow back into the compressor 110 again via the gas return port 112.

A theoretical calculation for the air conditioning system enforcing the APF Grade III and APF Grade I conditions of the Chinese APF standard is performed below, in which a condensing temperature is Tc, an evaporating temperature is Te, a condenser outlet temperature is Tco and a suction temperature is Ts. The values of the condensing temperature, the evaporating temperature, the condenser outlet temperature and the suction temperature under the Chinese APF Grade III and APF Grade I conditions may refer to the parameters below:

Chinese APF Grade III Work conditions Tco Tc Te Ts Rated refrigerating 46 52 7.2 18.3 Intermediate refrigerating 35 43 16 22 Rated heating 38 45.9 −0.3 9.7 Intermediate heating 22 30 2.7 13.8 Low-temperature heating 34.3 42.3 −10.7 5

Chinese APF Grade I Work conditions Tco Tc Te Ts Rated refrigerating 41 46 10 18 Intermediate refrigerating 35 38 20 26 Rated heating 34.3 42.3 2.7 12.8 Intermediate heating 22 30 2.7 13.8 Low-temperature heating 34.3 42.3 −10.7 5

For example, when the refrigerant is R410A, the calculation results of the air conditioning system 100 according to embodiments of the present invention are as follows:

Chinese APF Grade III Exhaust Optimal volume Work energy ratio conditions Tco Tc Te Ts efficiency V2/V1 Rated 46 52 7.2 18.3 4.91 0.08 refrigerating Intermediate 35 43 16 22 8.78 0.07 refrigerating Rated heating 38 45.9 −0.3 9.7 4.79 0.09 Intermediate 22 30 2.7 13.8 8.45 0.04 heating Low-temperature 34.3 42.3 −10.7 5 3.99 0.07 heating

Chinese APF Grade I Exhaust Optimal volume Work energy ratio conditions Tco Tc Te Ts efficiency V2/V1 Rated 41 46 10 18 6.33 0.10 refrigerating Intermediate 35 38 20 26 12.92 0.04 refrigerating Rated heating 34.3 42.3 2.7 12.8 5.74 0.07 Intermediate 22 30 2.7 13.8 8.45 0.04 heating Low-temperature 34.3 42.3 −10.7 5 3.99 0.07 heating

The calculation results prove that: when the ratio of the exhaust volume V2 of the second cylinder to the exhaust volume V1 of the first cylinder is smaller than 10%, the air conditioning system 100 reaches the optimal performance easily.

An air conditioner according to embodiments of the present invention includes the above-described air conditioning system 100.

For the air conditioner according to embodiments of the present invention, by providing the above-described air conditioning system 100 and making the exhaust volume ratio of the second cylinder to the first cylinder smaller than or equal to 0.1, the performance of the air conditioning system 100 may be effectively improved, and the air conditioner may reach the state with the optimal energy efficiency easily.

In the description of the present specification, the reference terms “an embodiment”, “some embodiments”, “an exemplary embodiment”, “an example”, “a specific example”, or “some examples” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. Thus, the appearances of the phrases in various places throughout this specification are not necessarily referring to the same embodiment or example of the present disclosure. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

Although explanatory embodiments have been shown and described, it would be understood by those skilled in the art that changes, alternatives, modifications and variants can be made in the embodiments without departing from principles and spirit of the present invention, and the scope of the present invention are defined by the claims and their equivalents. 

1. An air conditioning system, comprising: a compressor comprising a first cylinder, a second cylinder, an exhaust port and a gas return port, a gas compressed by the first cylinder and the second cylinder being discharged from the exhaust port, wherein an exhaust volume of the first cylinder is V1, an exhaust volume of the second cylinder is V2, and the V1 and V2 meet: V2/V1≤0.1; an outdoor heat exchanger comprising a first inlet and a first outlet, and an indoor heat exchanger comprising a second inlet and a second outlet, the first outlet being in communication with the second inlet; a directional control assembly comprising a first valve port, a second valve port, a third valve port and a fourth valve port, wherein the first valve port is in communication with the exhaust port, the fourth valve port is in communication with the gas return port, the second valve port is in communication with the first inlet, and the third valve port is in communication with the second outlet; a first throttling element and a second throttling element connected in series between the indoor heat exchanger and the outdoor heat exchanger; a gas-liquid separator comprising a first opening, a second opening and a gas outlet, wherein when the air conditioning system is refrigerating, the first valve port is in communication with the second valve port, the third valve port is in communication with the fourth valve port, the first opening is in communication with the first throttling element, the second opening is in communication with the second throttling element, and the gas outlet is in communication with the second cylinder via a medium-pressure suction pipe; when the air conditioning system is heating, the first valve port is in communication with the third valve port, the second valve port is in communication with the fourth valve port, the first opening is in communication with the second cylinder via the medium-pressure suction pipe, the second opening is in communication with first throttling element, and the gas outlet is in communication with the second throttling element; and a liquid reservoir, wherein one end of the liquid reservoir is in communication with the fourth valve port, and the other end thereof is in communication with the gas return port via a low-pressure suction pipe.
 2. The air conditioning system according to claim 1, wherein the V1 and V2 meet: V2/V1≤0.09.
 3. The air conditioning system according to claim 2, wherein the V1 and V2 meet: 0.04≤V2/V1≤0.08.
 4. The air conditioning system according to claim 3, wherein the V1 and V2 meet: 0.04≤V2/V1≤0.07.
 5. The air conditioning system according to claim 3, wherein the V1 and V2 meet: 0.07≤V2/V1≤0.08.
 6. The air conditioning system according to claim 1, wherein the directional control assembly is a four-way valve.
 7. The air conditioning system according to claim 1, wherein the compressor is a gaseous refrigerant injection type compressor.
 8. An air conditioner, comprising an air conditioning system comprising: a compressor comprising a first cylinder, a second cylinder, an exhaust port and a gas return port, a gas compressed by the first cylinder and the second cylinder being discharged from the exhaust port, wherein an exhaust volume of the first cylinder is V1, an exhaust volume of the second cylinder is V2, and the V1 and V2 meet: V2/V1≤0.1; an outdoor heat exchanger comprising a first inlet and a first outlet, and an indoor heat exchanger comprising a second inlet and a second outlet, the first outlet being in communication with the second inlet; a directional control assembly comprising a first valve port, a second valve port, a third valve port and a fourth valve port, wherein the first valve port is in communication with the exhaust port, the fourth valve port is in communication with the gas return port, the second valve port is in communication with the first inlet, and the third valve port is in communication with the second outlet; a first throttling element and a second throttling element connected in series between the indoor heat exchanger and the outdoor heat exchanger; a gas-liquid separator comprising a first opening, a second opening and a gas outlet, wherein when the air conditioning system is refrigerating, the first valve port is in communication with the second valve port, the third valve port is in communication with the fourth valve port, the first opening is in communication with the first throttling element, the second opening is in communication with the second throttling element, and the gas outlet is in communication with the second cylinder via a medium-pressure suction pipe; when the air conditioning system is heating, the first valve port is in communication with the third valve port, the second valve port is in communication with the fourth valve port, the first opening is in communication with the second cylinder via the medium-pressure suction pipe, the second opening is in communication with first throttling element, and the gas outlet is in communication with the second throttling element; and a liquid reservoir, wherein one end of the liquid reservoir is in communication with the fourth valve port, and the other end thereof is in communication with the gas return port via a low-pressure suction pipe.
 9. The air conditioner according to claim 8, wherein the V1 and V2 meet: V2/V1≤0.09.
 10. The air conditioner according to claim 9, wherein the V1 and V2 meet: 0.04≤V2/V1≤0.08.
 11. The air conditioner according to claim 10, wherein the V1 and V2 meet: 0.04≤V2/V1≤0.07.
 12. The air conditioner according to claim 10, wherein the V1 and V2 meet: 0.07<V2/V1≤0.08.
 13. The air conditioner according to claim 8, wherein the directional control assembly is a four-way valve.
 14. The air conditioner according to claim 8, wherein the compressor is a gaseous refrigerant injection type compressor. 